KR20030004080A - Bearing unit in the form of bushing - Google Patents

Abstract

The present invention relates to a bushing-type bearing unit 1 having an outer ring 2 and a support 4 and rubber springs 5 and 6 disposed therebetween, in which case the outer ring 2 At least in the connecting regions 8, 9 of the rubber springs 5, 6 are preferably provided recesses 10, 11 in the main load direction 7, which recesses 10, 11 have an outer ring ( Convex ends 12, 13 are provided which are located above the outer contour of 2).

Description

Bushing Bearing Unit {BEARING UNIT IN THE FORM OF BUSHING}

The present invention relates to a bushing bearing unit having an outer ring and a support and a rubber spring disposed therebetween.

In known bearing units of this kind the rubber spring is vulcanized in the gap between the outer ring and the support. This process has the property that shrinkage of the rubber spring occurs upon cooling of the bearing following the vulcanization, which in turn results in an enlargement of the gap, which is negatively related to the desired bearing characteristics. May affect

In order to avoid the above mentioned disadvantages it is known from DE 38 40 176 C2 to insert an adduct into the enlarged gap, whereby an elastic initial stress is obtained. By the above measures, the movement in the tension direction of the bearing is started early. By Kalibrierung, the bearing unit can be formed and inserted without the additions. The correction should also eliminate the gap in whole or at least in part. This causes problems when the gap has a relatively large size, for example up to 4 mm. In this case the size of the gap consists of two parts, namely the already mentioned shrinkage size of up to 2 mm in size order and the smallest size inevitably produced in the manufacturing technique in axial penetration of the rubber spring. The correction becomes particularly difficult when the outer ring is provided with a cut elastomeric sheath.

It is an object of the present invention to provide a bearing unit which can be manufactured inexpensively and which avoids the disadvantages which arise in rubber springs due to shrinkage.

1 is a cross sectional view of a bearing unit in symmetrical tensile / compressive stress,

2 is a longitudinal sectional view of the bearing unit of FIG. 1,

3 is a cross-sectional view of the bearing unit in the operating path in the radial direction,

4 is a longitudinal cross-sectional view of the bearing unit of FIG. 3,

5 is a plan view of the bearing unit of FIG.

6 is a cross-sectional view of the bearing unit of FIG. 3, embedded in a holder,

7 is a longitudinal sectional view of the bearing unit of FIG. 6,

8 is a cross sectional view of a bearing unit with an additional cross path boundary,

9 is a cross-sectional view of the bearing unit of FIG. 8 in an embedded state,

10 is a cross-sectional view of another formation of the bearing unit.

* Description of the symbols for the main parts of the drawings *

1: bearing unit 2: outer ring

3: elastomer sheath 4: internal support

5, 6: Rubber spring 7: Main load direction

8, 9: connection area 10, 11: recess

12, 13: convex ends 14, 15: slope formation

16: tension stop 17: through part

18, 19: V-shaped spring 20: crimp stop buffer

21: area of the outer ring 22: recess

23: convex end 24: ridge

25: holder 26, 27: additional recess

28, 29: arch portion 30, 31: side stop

35, 36: recess 37, 38: spring leg

39, 40: convex end 41: stop

X: thickness

This object is achieved according to the invention in the case of a bearing unit of the aforementioned kind, wherein the outer ring of the bearing unit is provided with a recess in the direction of the main load at least in the connection region of the rubber spring, the recess being outside of the outer ring. A convex end is provided that is located above the contour. The new arrangement prioritizes the use of an outer ring, which is covered with an elastomer, thereby saving a relatively expensive corrosion protection cost in the case of a metal ring which is not covered with an elastomer as the outer ring. By applying radially projecting convex ends, excessive correction is omitted. While the bearing is embedded in the holder, the convex end is squeezed radially inward by the recess in the outer ring, so that the shrinkage of the rubber spring is lost or even the initial stress of the rubber spring is obtained. For this purpose, the spacing between the top of the convex end and the outer contour of the outer ring is chosen to be equal to or greater than the shrinkage size created by the vulcanization of the rubber spring. The concept of the present invention therefore forms a rubber spring of at least one bearing so that the convex end of the rubber spring is inserted through the recess in the outer ring, and after the bearing is installed in the holder, the recess is radially inward. Is compressed so that at least the shrinkage size is removed. If the height and shape of the convex ends are the same, the initial stress can be exerted up to the rubber spring, which is preferable in case of continuous use.

In pursuit of the idea of the invention, a convex portion may be provided on the side of the outer ring away from the spring. The convex portion is separated from the rubber spring in the present invention. The bearing is embedded in the holder, whereby the convex ends are thus compressed in the radial direction into the recesses in the outer ring, thereby filling the extension of the separation gap due to the inevitable free path and contraction in production. The convex end again adjoins the inner support. In the present invention the outer ring is provided with a recess equal to the quantity of the region in the region or regions of the minimum free spacing inevitably produced between the outer ring and the inner support. At the same time, the elastomeric sheath in the outer ring has a bulge in the area to fill at least the space inevitably produced between the outer ring and the support in the bearing in which the bulge is assembled.

In order to produce a stable and concentric bearing unit, the elastomeric sheath in the outer ring is provided with a ridge on its outer surface in a known manner. The ridge proceeds in the axial direction of the outer ring, for example in the form of a wave.

In order to further delimit the free path of the inner support opposite the main load direction, an additional recess is provided in the wall of the outer ring located on the side of the main load direction, the additional recess being covered by the arch of the elastomeric sheath. And in the assembled state they are pressed against the outer ring radially inward. In general, the arch is identical in shape to the convex end described above, and in the same way can be pressed against the bearing radially by a recess in the outer ring. Therefore, this makes it possible for the same formed stops to act earlier, as opposed to the main load direction.

The invention is illustrated in detail by the embodiments shown in the drawings.

In Fig. 1 the bearing unit 1 formed in the form of a bushing is shown in cross section, although not in an assembled state. The bearing unit consists essentially of an outer ring 2 with an elastomeric shell 3, an inner support 4 and rubber springs 5, 6. In the bearing 1 in operation, the force exerted in the load direction 7 is shown by an arrow. The connection regions 8, 9 of the rubber springs 5, 6 are provided with recesses 10, 11 in the outer ring 2. The recesses 10, 11 allow the rubber springs 5, 6 to penetrate through the convex ends 12, 13 and protrude above the outer contour of the outer ring formed by the elastomeric shell 3. . The distance X between the convex end top and the outer contour of the outer ring 2 is selected to be at least equal to the shrinkage size of the rubber springs 5, 6. The convex ends 12, 13 are substantially drawn into the recesses 10, 11 of the outer ring by contraction of the springs 5, 6, as long as they coincide with the springs 5, 6 in height. Enter Also preferably, the gap size X is chosen to be larger so that the initial stresses can already be exerted on the springs 5, 6 when the bearing unit 1 is embedded in the holder.

In figure 2 a longitudinal section of the bearing of figure 1 is shown. In this figure, the longitudinal extension of the rubber springs 5, 6 and on the left side of the figure, the arrangement of convex ends 12, 13, denoted by reference numerals 14 and 15, formed similarly to a slope, can be seen. This makes it easier to embed the bearing 1 in its holder.

3 shows a cross section of the bearing unit 1 moving in the main load direction 7. The tension stop 16 is formed in the form of a piece in this embodiment. Elasticity is generally due to the V-shaped springs 18, 19 seen in the cross section above. Between the springs 18 and 19 there is a crimping stop buffer 20. In the region 21 a recess 22 is provided in the outer ring 2. The recess 22 is covered by a convex end 23 provided in the outer ring 2. The rubber springs 18, 19 are attached to the outer ring 2 straight on the side, even in the absence of recesses in the outer ring. When the bearing 1 is embedded in a holder, the convex end 23 is pressed into the recess 22 and abuts against the outer surface of the stop 16 lying radially. In this way not only the shrinkage size created by the contraction of the springs 18, 19 when the bearing is embedded in the holder, but also the free path created by the existing axial through 17 can be covered.

4 shows a longitudinal section of the bearing 1 in which an axial through 17 is formed. The stop 16 is separated from the convex end 23 by the axial through 17. Nevertheless, in order for the above process to start early in the tensioning direction, the bearing 1 is pressed inward when embedded in the holder, and the convex end 23 whose inner surface is adjacent to the stop 16 is Is provided. The springs 18, 19 extend in this embodiment over the entire axial length of the bearing. Nevertheless, if the convex end 23 acting together with the stop 16 extends only over the length of the recess 21, it is sufficient for its intended reference progression.

FIG. 5 is a plan view of the bearing of FIGS. 3 and 4 where the shape of the convex end 23 and the recess 22 can be seen. The ridge 24 in the elastomeric shell 3 of the outer ring 2 is also clearly visible. The convex end 23 covers the concave portion 22 inclined toward the top, as seen in the figure. As a result, the bearing 1 is easily inserted into the holder.

6 and 7 are cross-sectional and longitudinal cross-sectional views of the bearing 1 embedded in the holder 25. The convex end 23 is compressed by the recess 22 and is adjacent to the stop 16.

In Figures 8 and 9 there is shown a configuration with a free path created by the axial through 17 and in which the boundary must be set. In Fig. 8 the finished bearing 1 is shown, and in Fig. 9 the bearing 1 is shown in an embedded state. The formation of the outer ring 2 and the interior 4, in which the springs 18 and 19 and the convex ends 23 and the recesses 22 are included, is common with the formation according to FIGS. 3 to 7. In addition to this the outer ring 2 has further recesses 26, 27 in the wall which are located on the side of its main load direction 7. The further recess is covered by the arches 28, 29 of the elastomeric sheath 3, as seen in FIG. 9, in the same manner as in the case of the convex end, in the assembled state, in a radial manner. Is pressed against the outer ring 2. The interior 4 is provided with side stops 30 and 31 to which the arches 28 and 29 abut in an assembled state. In this way an additional boundary to the free path can be set on the bearing 1 in the transverse direction.

In FIG. 10 a cross section is shown for another formation of the bearing 1. In this case the recesses 35, 36 are located on the lower half of the outer ring 2. On the lower half there are spring legs 37, 38 of rubber springs formed in a V shape. The convex ends 39, 40 protrude above the outer contour of the outer ring 2. The bearing 1 is embedded in the holder, so that the pressed portions 4, 40 are pressed against the stop portions 41, which protrude upwards inward. The spacing between the support 4 and the stop 41 is equal to the shrinkage produced by cooling and through-through 17 inevitably produced during manufacture of the bearing 1. The formation of the bearing 1 is the same as that described in FIG. 3, but only on the other side.

The concept of the invention can also be applied to bearing units with an outer ring without elastomeric sheath, for example when corrosion protection or resistance control is not required.

According to the present invention, a bearing unit is provided which is inexpensively manufactured and which avoids the disadvantages that occur in rubber springs due to shrinkage.

Claims (7)

In a bushing bearing unit 1 having an outer ring 2 and a support 4 and rubber springs 5 and 6 disposed therebetween, The outer ring 2 is provided with recesses 10, 11 at least in the connecting regions 8, 9 of the rubber springs 5, 6, and the recesses 10, 11 of the outer ring 2. Bearing unit, characterized in that a convex end (12, 13) is provided that lies above the outer contour. The method of claim 1, The recess (10, 11) is a bearing unit, characterized in that provided in the main load direction (7). The method of claim 1, The bearing (X) between the convex end top and the outer contour of the outer ring (2) is equal to the shrinkage size of the rubber spring (5, 6) produced by vulcanization. The method of claim 1, Bearing space, characterized in that the distance (X) between the convex end top and the outer contour of the outer ring is greater than the shrinkage size of the rubber spring (5, 6). The method according to any one of claims 1 to 4, Bearing unit, characterized in that the outer ring (2) is provided with an elastomeric sheath (3). The method of claim 5, The outer ring 2 has a quantity equal to the quantity of the region 21 within the freely spaced regions or regions 21 inevitably produced between the outer ring 2 and the inner support 4. A recess 22 is provided and the elastomeric shell 3 in the outer ring 2 has a bulge in the region 21, so that the outer ring 2 in the bearing 1 in which the bulge is assembled. And a space (17) inevitably produced in manufacturing between the support and the support (4). The method of claim 5, On the wall located in the main load direction 7 side of the outer ring 2, an additional recess is provided, which is covered by the arches 28, 29 of the elastomeric shell 3 and assembled In the state radially inwardly pressed against the outer ring and forming a boundary of the free path of the inner support (4).